Power driving device for a calculating machine



' 3,331,556 POWER DRIVING DEVICE FOR A CALCULATING MACHINE Filed Nov. 9,1965 T- GASSINO July 18, 1967 4 Sheets-Sheet l INVENTOR. TERESIO GASSINOAGENT y 8 967 T. GASSINO 3531,55

POWER DRIVING DEVICE FOR A CALCULATING MACHINE Filed Nov. 9, 1965 4Sheets-Sheet 2 LLL II u H INVENTOR. TERESIO GASSINO AGENT T. GASSiNOJuly 1, w

4 Sheets-Sheet 5 Filed Nov. 9, 1965 INVENTOR.

TERESIO GASSINO AGENT T. GASSINO 3,33

POWER DRIVING DEVICE FOR A CALCULATING MACHINE 4 Sheets-Sheet 4 FiledNov. 9, l95

INVENTOR. TERESIO GASSINO 3,331,556 POWER DRIVING DEVICE FGR ACALCULATING MACHINE Teresio Gassino, Ivrea, Torino, Italy, assignor toling. C.

a corporation of Italy This invention relates to a power driving devicefor a printing calculating machine having a set of differentiallyreciprocable actuators, comprising a first cyclically power Operatingmechanism for said actuators, said first mechanism being normallyadapted to be operated at a predetermined speed sequentially with asecond cyclically power operating mechanism for effecting predeterminedmachine functions.

There are known calculating machines wherein some machine functions, forexample the operation of the totalizer reversing device and the clearingof the set up device, are effected by mechanisms cyclically operableindependent from the mechanism for cyclically operating the actuators.However there are cases wherein some functions are not to be effected,as for example the case a of repeated cycles of a multiplication or adivision Wherein no printing is effected and the set up device is notcleared. Since in the known calculating machines the mechanism foroperating the actuators is always operated at a constant speed, thesemachines have a relatively unsatisfactory speed in the above specificcycles. In another known calculating machine of the Thomas drum typeprovided with a printing device, the calculating shaft may be operatedat a lower speed when the printing device is to be operated, the timerequired by the printing device being longer than that required by thecalculating device. This known driving device is unadapted for printingcalculating machines having reciprocable actuators because in saidmachines the type carriers of the printing device are controlled by theactuators during their actuating reciprocation, said typecarriers beingthen moved toward the paper while the actuators rest in their reachedposition.

In a further known calculating machine the speed of the electric motormay be increased in specific cases. However since the speed of thevarious mechanisms is increased according to a constant ratio, themachine is not reliable in the operation.

To obviate these disadvantages in a printing calculating machinecomprising a set of differentially reciprocable actuators, a powerdriving device having a main shaft cyclically power operable through aone-revolution main clutch for operating said actuators, an auxiliaryshaft cyclically power operable through a one-revolution auxiliaryclutch for effecting predetermined machine functions, and a memberoperated by said auxiliary shaft for causing said main shaft to beoperated and for temporarily arresting said auxiliary shaft in anintermediate position, I now provide a normally effective first mainclutch for driving said main shaft at a predetermined angular speed, anormally ineffective second main clutch for driving said main shaft atan angular speed higher than said predetermined angular speed, a firstgroup of cams on said main shaft, a group of cam followers nor' mallycooperating with said first group of cams for controlling said machinefunctions in a predeterminate timing relationship with respect to theangular position of said main shaft, means operable for displacing saidmain shaft in an axial direction for rendering said first main clutchand said first group of cams ineffective and for rendering said secondmain clutch effective, a function control member, a shifting membercontrolled by said 333L556 Patented July 18, 1967 control member andoperated by said auxiliary shaft for operating said displacing means,and a second group of cams on said main shaft adapted to cooperate withsaid cam followers when said main shaft is so displaced for controllingsaid machine function in a different timing relationship with respect tothe angular position of said main shaft.

This and other characteristics of the invention will become apparentfrom the following detailed description of a preferred embodimentthereof made by way of example, and from the accompanying drawings,wherein:

FIG. 1 is a left hand longitudinal partial sectional view of acalculating machine incorporating a power driving device according tothe invention;

FIG. 2 is another left hand partial sectional view of the machine;

FIG. 3 is a partial plan view of the machine;

FIG. 4 is a further left hand partial sectional view of the machine;

FIG. 5 is a partial sectional view taken according to the line V-V ofFIG. 3;

FIG. 6 is a partial sectional view taken according to the line VIVI ofFIG. 3;

FIG. 7 is a frontal view of a detail of the machine.

General description The power driving device is incorporated in a tenkey printing calculating machine comprising a set up carriage 11(FIG. 1) transversely movable step by step along a square shaft 12rockably mounted on the machine frame, and along a shaft 13 verticallymovable on said frame. The carriage 11 comprises a set of toothedsectors 14 rotatably and shiftably mounted in the shaft 13 anddifferentially settable clockwise from the zero position shown inFIG. 1. The carriage 11 is urged by a spring 16 (FIG. 3) rightwards andit is provided with a projection 17 entering a notch of a rack 18transversely slidable on a square shaft 19 rockably mounted on themachine frame. The rack 18 normally engages a pinion 21 secured to ashaft 22 rotatably mounted on the machine frame and normally lockedagainst the urge of the spring 16 by a latch 24 engaging another pinion23 secured to the shaft 22.

Bodily rotatable with the shaft 22 is a hub 25 (FIG. 6) axially slidablethereon. The hub 25 is integral with a conic clutch driving member 26adapted to cooperate with a clutch driving member 27 continuouslyrotated by a conventional electric motor of the machine not shown in thedrawings. The clutch 26, 27 is controlled by a lever 28 secured to ashaft 29 rotatably mounted on the machine frame. Secured to the shaft 29is also a second lever 30 normally urged clockwise by a spring 31, as todisengage the clutch 26, 27. A latch 34 fulcrumed on a pivot 35 isnormally urged by a spring 33 to contact a lug 32 of the lever 28. Thelatch 34 is provided with a projection 36 cooperating with an arm 37(FIG. of a bail 38 fulcrumed on a vertical shaft 39. Another arm 41 ofthe bail 38 is normally urged by a spring 42 to contact a projection 43of a transversely slidable slide 44 (FIG. 1).

The shaft 22 is adapted to transversely displace a rack 42 along a shaft52 through a pair of bevel gears 46, a vertical shaft 47 and a pinion48. The rack 49 is provided with a toothed edge 50 cooperating with asector 51 bodily rotatable with the shaft 52, but axially slidable withrespect thereto. As long as the rack 18 engages the pinion 21, the rack49 is transversely located according to the transverse position of thecarriage 11.

The sectors 14 may be set order by order by a cyclical- 1y operatingshaft 53 under the control of the ten key keyboard. Fulcrumed on a cam54 (FIG. 6) of the shaft 53 is a clutch pawl 56 adapted to engage aclutch wheel 57 rotatably mounted on the shaft 53 and continuously 3rotated clockwise by the electric motor of the machine. A lug 58 of abail 59 fulcrumed at 60 normally holds the pawl 56 disengaged from thewheel 57. The bail 59 is provided with an arm 61 pin and slot connectedwith a slide 62 having a bent lug 63 normally urged by a spring 64 tocontact a projection 65 of a link 66. The slide 62 is linked with a bail67 fulcrumed on a stationary shaft 68. The spring 64 urges the bail 67counterclockwise and the bail 59 to contact the cam 54. Finally, theslide 62 is provided with a pin 69 adapted to cooperate with another cam70 of the shaft 53.

The link 66 is rearwards linked with the lever 30 and is normally urgedby a spring 71 to contact a pin 72 of a lever 73 fulcrumed on a pivot74. The lever 73 is located in the position of FIG. 6 upon effecting anaccumulating or total taking operation, whereas it is rockedcounterclockwise to the position shown by broken lines upon setting upin the carriage 11 the first order of a new amount, substantially in themanner described in the applicants United States Patent application,Ser. No. 398,915 dated September 24, 1964. The link 66 is also providedwith a projection 75 adapted to cooperate with a lug 76 of a lever 77fulcrumed on a pivot 78 and urged by a spring 79 to contact a cam 81secured to the shaft 53.

When the lever 73 is located in the position of FIG. 6, the projection75 is located below the path of the lug 76. Upon depressing each key onthe ten key keyboard, the bail 67 is rocked clockwise and displaces theslide 62 rearwards. The lug 63 of the slide 62 disengages now theprojection 65 of the link 66, while the bail 59 is rockedcounterclockwise, thus causing the clutch 56, '57 to be engaged for aone-revolution set up cycle of the shaft 53. At the beginning of thefirst set up cycle the lever 73 is rocked to the position shown bybroken lines. The link 66 is thus displaced upwards by the pin 72 of thelever 73 and places its projection 75 on the path of the ing 76 of thelever 77.

During this first set up cycle, as well as during the following set upcycles, the figure corresponding to the depressed key is set up on asector 14 of the carriage 11. Thereafter the cam 81 (FIG. 6) rocks thelever 77 counterclockwise, whereby the lug 76 through the projection 75displaces the link 66 forwards. The lever 30 is thus rockedcounterclockwise together with the shaft 29 and the lever 28, thusengaging the clutch 26, 27, while the latch 34 latches its lugs 32 inthe rocked position. Simultaneously, under the control of the lever 73the shaft 52 (FIG. 1) is rocked counterclockwise to temporarilydisengage the sector 51 from the toothed edge 50, and then to return toan intermediate position wherein it is reengaged with the next followingtooth of the edge 50 and may cooperate with a lug 82 of the slide 44.

Now, when the sector 51 encounters the lug 82, the bail 38 (FIG. 3) isrocked clockwise thus rocking the latch 34 (FIG. 6) counterclockwise.Then the spring 31 through the levers 30 and 28 causes the clutch 26, 27to be disengaged, upon having displaced the rack 49 (FIG. 1) one stepleftwards together with the carriage 11. At the end of the cycle, thecam 70 (FIG. 6) engages the pin 69, thus restoring the slide 62 whichlatches its lug 63 above the projection 65 of the link 66.

As it has been described in the cited patent application, at the end ofany accumulating operation the sectors 14 (FIG. 1) of the carriage -11return to the set position until a new amount will be set up, whereasthe carriage 11 is transversely restored rightwards by the spring 16(FIG. 3) upon causing the latch 24 to release the pinion 23. Since thelever 73 has been returned to the position of FIG. 6, the rack 49displaces rightwards the sector 51, which thus represents a record ofthe number of orders set up on the carriage 11.

The square shaft 12 is adapted to be rocked clockwise to engage thesetup sectors 14 with a set of difierentially reciprocable actuators,each one formed of a rack 83 longitudinally slidable on a pair ofstationary shafts 84.

The racks 83 are also adapted to cooperate with a totalizer 86, and arecontrolled by a first universal bar 87 secured to a bail 88 fulcrumed at89. A projection 93 of a rack 94 is normally urged by a spring 92 tocontact a pin 91 secured to the bail 88. The rack 94 is slidably mountedon the shafts 84 and engages a toothed sector 96 fulcrumed on astationary pin 97, and pin and slot connected with an arm 98 secured tothe shaft 13. A second universal bar 101] is secured to a pair of arms99 bodily rockable and axially slidable on the shaft 13, and it isadapted to cooperate with a shoulder 101 provided on each sector 14.

Furthermore, the calculating machine comprises a printing deviceconditionable for printing amounts according to the differentialreciprocation of the racks 83. To this end each rack 83 is provided witha pin 103 adapted to cooperate with a notch 104 of a corresponding lever106 fulcrumed on a stationary shaft 107. Each lever 166 is normallyurged by a corresponding spring 1118 to contact another universal bar109 secured to a pair of arms 111 fulcrumed on the shaft 107. Each lever106 is adapted to predispose through a rack 112 a correspondingtypewheel 113 fulcrumed at 114 on a printing hammer 116 adapted to bringthe wheel 113 to effect an imprint on the conventional paper platen 117.

Driving device speed, said first means comprising a pinion 126 engaginga gear 124 secured to a shaft 123 continuously rotated clockwise by theelectric motor. Furthermore, second means are provided for operating theshaft 121 (FIG. 4) at a higher speed, said second means comprising apinion 119 rotatably mounted on the shaft 121 and engaging another gear124 secured to the shaft 123. The diameter of the pinion 119 is such asto cause same to be rotated at a speed twice the speed of the pinion126. The pinion 119 engages also a gear 118 secured to the wheel 57(FIG. 3). Secured to the shaft 123 is also a pinion 127 (FIG. 4)engaging a similar pinion 128 rotatably mounted on a third cyclicallyoperable shaft 129. The pinion 128 is rotated at a speed twice the speedof the pinion 126, whereas the pinion 118 is rotated at a speed twiceand the half the speed of the pinion126.

Secured to the main shaft 121 (FIGS. 1 and 3) is a first group of camscomprising a pair of earns 131, 132 normally cooperating with the bail88, and a cam 133 normally cooperating with a lever 134 fulcrumed on apivot 136 and pin and slot connected with the right arm 111. The shaft121 (FIG. 6) is adapted to be operated through a main clutch comprisinga clutch wheel 142 secured to the pinion 126 (FIG. 3) and a clutch pawl141 formed on a bail 138. This latter is fulcrumed on a crank lever 137secured to the shaft 121v (FIG. 6) and is connected thereto by a spring139.

The bail 138 is provided with a projection 146 normally arrested by alug 143 of a clutch control lever 144 fulcrumed on a stationary shaft148. Therefore, the pawl 141 normally disengages the wheel 142, whereasa shoulder 147 of the lever 137 contacts the bail 138. The lever 144 isprovided witha pin 149 cooperating with a cam 151 of the shaft 121.Furthermore the lever 144 is provided with a lug 152 adapted tocooperate with the clutch pawl 56 for arresting same in an intermediateposition, but it is normally out of the path of the pawl 56.

The calculating machine is provided with a second cyclically operatingmechanism comprising a sleeve 153 rotatably mounted on the shaft 53 andadapted to be bodily rotated therewith toeffect an auxiliary cyclesequentially with the main cycle of the shaft 121. Therefore, the shaft53 will be hereinafter called auxiliary shaft, whereas the clutch 56, 57will be called auxiliary clutch. The sleeve 153 is provided with aprojection 158 (FIG. 4) normally engaging a notch 157 formed on an arm156 of a bail 154 fulcrumed on the shaft 148, Another arm 159 of thebail 154 is provided with a circular hole 161 cooperating with a pair oflugs 160 bent from a pawl 162. This latter is fulcrumed on a crank lever163 secured to the sleeve 153.

The sleeve 153 is provided with a set of cams adapted to control a setof machine functions,- for example for engaging and disengaging thesectors 14 with the racks 83, and for returning the set up carriages 11rightwards, said functions being not eifected in the set up cycles ofthe auxiliary shaft 53. Secured to the sleeve 153 is also a cam 166(FIG. 6) cooperating with a bail 168 fulcrumed on the shaft 148 andurged counterclockwise by a spring 167. Fulcrumed on a pivot 169 of thelever 168 is a lever 171 connected thereto by a spring 172 and providedwith a cam slot 173 entered by a pin 174 of the lever 144.

The shaft 129 (FIG. 4) is adapted to be rotated through a correspondingone-revolution clutch comprising a clutch wheel 176 secured to thepinion 128 and a clutch pawl 177 fulcrumed on a crank lever 178 securedto the shaft 129. The pawl 177 is normally arrested by a lug 179 of alever 181 fulcrumed on a stationary pivot 182 and provided with aprojection 183 normally urged by a spring 184 to contact a pin 185 of alever 186 fulcrumed on the shaft 148. The lever 186 is provided with alug 187 normally urged by a spring 188 to contact a projection 189 of aslide 191. A pin 192 of a lever 193 pivoted at 194 is normally urged bythe spring 188 to contact a vertical edge of the projection 189. Thelever 193 is provided with a lug 195 adapted to cooperate alternatelywith each one of a pair of shoulders 196 and 197 of the lever 186, thelug 195 being normally located into the path of the shoulder 197.

Secured to the shaft 129 is a first cam 198 (FIG. 6) cooperating withthe lever 30, and a second cam 199 (FIG. 4) cooperating with a lever 201fulcrumed on a pivot 202 and urged clockwise by a spring 200. A lug 203of the lever 201 is adapted to engage both a projection 204 of the lever186 and another arm 206 of the bail 154. The slide 191 is provided witha slot 207 slidable on a pin 208 and is linked at 209 with a startingmember formed of a slide 211. This slide is also linked at 212 with thearm 156 of the bail 154, and at 213 with an arm 214 secured to a shaft216 rotatably mounted on the machine frame. The arm 214 is normallyurged by a spring 217 to contact a stationary stop 218.

Furthermore, the slide 211 is provided with a projection 219 adapted toengage a pin 221 (FIG. 6) of a lever 222 fulcrumed on a pivot 223 andpin and slot connected with the lever 73. Finally, the slide 211 isprovided with a projection 224 (FIG. 4) adapted to cooperate with alatch 226 (FIG. 7) pivoted at 227 on a transverse slide 228. This latteris provided with a pair of slots 229 entered by a pair of stationarypins 231, and is normally urged by a spring 232 to contact a portion 233of the set up carriage 11. The slide 228 when released by the portion233 is displaced leftwards by the spring 232 thus causing the latch 226to engage the projection 224 of the slide 211.

A universal bar 234 (FIG. 4) is secured to the arm 214 and to a secondarm 236 secured to the shaft 216 as well. The universal bar 234 isadapted to cooperate with a notch 237 of each one of a set of levers238, only one of which is shown in FIG. 4. Each lever 238 is fulcrumedon a common shaft 239 and is provided with a pin 241 cooperating with acam slot 242 of a stem 243 secured to a corresponding motor key, forexample the addition key 244. The other levers 238 are connected toother motor keys, for example the subtraction key, the total taking keyetc. Each lever 238 is also adapted to control specific machinefunctions.

At the depression of a motor key, for example the key 244, the cam slot242 of the corresponding stem 243 rocks the lever 238 partiallycounterclockwise. The notch 237 of the lever 238 through the universalbar 234 causes the arms 214 and 236 to be rocked counterclockwise,whereby the slide 211 is partially displaced rearwards. The bail 154 isthus slightly rocked clockwise without releasing the projection 158 ofthe sleeve 153. Furthermore, the slide 211 displaces rearwards the slide191, which on one hand causes the lug 195 of the lever 193 to contactthe edge of the lever 186, on the other hand its projection 189 releasesthe lug 187 thereof. Then the spring 188 rocks the lever 186 till theshoulder 197 is arrested by the lug 195 of the leve 193. The pin of thelever 186 rocks now the lever 181 clockwise, thus causing the clutch176, 177 to be engaged, whereby the shaft 129 begins a one-revolutioncycle.

At the beginning of the cycle of the shaft 129 its cam 199 rocks thelever 201 counterclockwise. Then the lug 203 of the lever 201 engagesthe arm 286 of the bail 154, which is now additionally rocked clockwise,thus fully displacing the slide 211 rearwards. The arm 156 of the bail154 releases now the projection 158 of the sleeve 153, while the arm 159through the lugs 168 causes the pawl 162 to engage the disk 164, wherebythe sleeve 153 is angularly secured to the auxiliary shaft 53. The slide211, through the arm 214 and the universal bar 234 additionally rocksthe lever 238 counterclockwise to control specific machine functions,but it no more affects the key 244, due to the shape of the cam slot242.

During the cycle of the shaft 129, some machine functions, for examplethe operation of the totalizer selecting mechanism and of the totalizerreversing mechanism, are effected under the control of the fully rockedlever 238. Furthermore the lug 20-3 of the lever 201 engages theprojection 284 thus rocking the lever 186 clockwise. The lever 186causes now its shoulder 196 to be latched by the lug of the lever 193,whereby the clutch 176, 177 cannot be reengaged before restoring theslide 191 forwards.

The slide 211 when fully displaced rearwards, through the projection 219engages the pin 221 of the lever 222, thus returning the lever 73 to theposition of FIG. 6 in the case it is not in said position. Thereafter acam of the shaft 129, not shown in the drawings, causes the sector 51(FIG. 1) to be rocked in a known manner to its intermediate position. Inturn the cam 198 of the shaft 129 (FIG. 6) rocks the lever 30counterclockwise, thus engaging the clutch 26, 27. The lever 30displaces also the link 66 forwards, thus predisposing its projection 65in front of the lug 63 of the slide 62.

In the case the carriage 11 (FIG. 1) is in its rightmost rest position,the clutch 26, 27 displaces the rack 49 leftwards until the sector 51encounters the lug 82, whereby the carriage 11 is tabulated to aposition corresponding to the amount set up therein. Now the carriageportion 232 releases the slide 228 (FIG. 7), thus placing the latch 226in front of the projection 224 of the slide 211. This latter is thusprevented from being restored as long as the carriage 11 will not bereturned rightwards. In the case the carriage 11 has been displaced fromits right position before starting the shaft 129, the latch 226 alreadycontacts the upper edge of the projection 224, whereby when the slide211 is fully displaced rearwards it is immediately latched by the latch226 in the reached position.

Upon the leftward movement of the rack 49, when the sector 51 (FIG. 1)encounters the lug 82, the slide 44 through the bail 38 (FIG. 6)disengages the latch 34 from the lever 28, thus causing the spring 31 torock the lever 31) clockwise. Now the link 66 is returned rearwards,whereby its projection 65 through the lug 63 displaces the slide 62rearwards. The bail 59 is thus rocked counterclockwise and causes theclutch 56, 57 to be engaged, whereby an auxiliary one-revolution cycleof the shaft 53 together with the sleeve 153 is started.

' It is to be noted that in the case the carriage 11 is already in thedue transverse position, the clutch 56, 57 is engaged before the end ofthe cycle of the shaft 129 under the mere control of the cam 198. On thecontrary, in the case the carriage 11 is to be tabulated through a longstroke, the engagement of the clutch 56, 57 may be delayed and may beeffected even after the shaft 129 terminates its cycle.

During a first part of the auxiliary cycle of the shafts 53 and thesleeve 153, some machine functions are effected, for example theengagement of the sectors 14 (FIG. 1) with the racks 83. Thereafter thecam 166 (FIG. 6) rocks the bail 168 clockwise, whereby the lever 171through the spring 172 yiel'dably rocks the lever 144. Then the lug 143of the lever 144 releases the projection 146 of the bail 138, thuscausing the pawl 141 to engage the wheel 142, whereby a one-revolutioncycle of the main shaft 121 is started. Simultaneously the lever 144locates its lug 152 on the path of the clutch pawl 56, whereby the shaft53 and the sleeve 153 will be temporarily arrested upon being rocked 270degrees, thus terminating the first part of the auxiliary cycle.

At the beginning of the cycle of the main shaft 121 (FIG. 1) thetotalizer 86 is engaged with the racks 83. Thereafter the cams 131 and132 rock the bail 88 counterclockwise, whereby through the rack 94 andthe sector 96 (FIG. 2), the universal bar 100 (FIG. 1) is caused toengage the projections 181 and returns the sectors 14 to their zeroposition. Then the sectors 14 positively displace the engaged racks 83rearwards, at the maximum permissible speed for correct accumulating theset up amount into the totalizer 86. Furthermore, the cam 133 of themain shaft 121, through the lever 134 rocks the universal bar 109clockwise, whereby the springs 108 urge the levers 106 to follow thepins 103 of the raoks 83. The typewheels 113 are thus predisposed forprinting the accumulated amount on the paper in a known manner.

Thereafter the totalizer 86 is disengaged from the racks 83. Then thecams 131 and 132 return the bail 88 clockwise, Whereby the universal bar87 returns the racks 83 positively to their zero position, while thesectors 14 are returned to the angular position they occupied at thebeginning of the cycle. Therefore, at the end of each cycle of the mainshaft 121 the printed amount remains set up into the sectors 14 of thecarriage 11. The tens transfer are effected in a manner known per se,during the return stroke of the racks 83.

Near the end of the cycle of the shaft 121, the cam 151 (FIG. 6) causesthe spring 167 to restore counterclockwise the lever 168 together withthe lever 144. Then the lug 143 of the lever 144 returns into the pathof the projection 146 of the bail 138, whereby the main clutch 141, 142will be disengaged upon having rotated the shaft 121 one revolution. Inturn the lug 152 of the lever 144 releases the clutch pawl 56, thuscausing the clutch 56, 57 to be reengaged for effecting a second part ofthe auxiliary cycle of the shaft 53 and the sleeve 153.

During this second part of the auxiliary cycle, at first the sectors 14(FIG. 1) are disengaged from the racks 83, and the sector 51 is returnedto the angular position of FIG. 1. Then the lever 24 is caused todisengage the pinion 23, whereby the spring 16 (FIG. 3) returns thecarriage 11 rightwards together with the rack 49 (FIG. 1) and the sector51. Furthermore, the carriage 11 through the slide 228 (FIG. 7) returnsthe latch 226 rightwards, thus releasing the projection 224 of the slide211.

At the end of the second part of the auxiliary cycle, the cam 71)returns the slide 62 upwards thus placing the lug 63 above theprojection 65 of the link 66. In turn the cam 54 causes the spring 64 torestore the slide 62 forwards while the bail 59 is restored clockwise,whereby 'the lug 58 will arrest the pawl 56, thus arresting theauxiliary shaft 53. The projection 158 (FIG. 4) of the sleeve 153returns now in front of the notch 157 of the arm 156, whereby the spring217 restores now the arm 214 together with the bar 234, the slide 211,the bail 154 and the slide 191. In turn the projection 189 of the slide191 returns into the path of the lug 187 of the lever 186.Simultaneously, the projection 189 engages the pin 192 of the lever 193to disengage the lug 195 from the shoulder 196, whereby the lever 186 isrestored to the position of FIG. 4. In turn the universal bar 234-releases the lever 238, which is finally restored by its spring togetherwith the key 244.

It is thus clear that the bail 168 and the lever 144 cause the shaft 121and 53 to be sequentially operated.

Specific machine operations, for example and correction of the amountset up on the carriage 11, do not require the movement of the racks 83-(FIG. 1), whereby the cycle of the main shaft 121 may be excluded. Inthis order a correction key not shown in the drawings is adapted to rocka lever similar to the lever 238 (FIG. 4), which is connected through alink 246 (FIG. 6) to a latch 247 fulcrumed on a stationary pivot 248.The latch 24-7 is adapted to cooperate with a lug 249 of the lever 144.

At the depression of the correction key, on one hand the universal bar234 (FIG. 4) is rocked counterclockwise thus causing the clutch 176, 177of the shaft 129' to be engaged, on the other hand the link 246 (FIG. 6)locates the latch 247 on the path of the lug 249. Then the shaft 129causes the clutch 56, 57 to be engaged, whereby the cam 166 of thesleeve 153 rocks the bail 168 clockwise. However the lever 144 isprevented from being rocked, because its lug 249 is arrested by thelatch 247. Therefore, the clutch 141, 142 is not engaged and the shaft121 is not cycled. Furthermore, the clutch 56, 57 is not disengaged bythe lug 152, whereby the two parts of the auxiliary cycle are effectedsequentially without being discontinued. During the second part of thiscycle the lever 24 (FIG. 1) is operated for causing the carriage 11 tobe restored in a similar manner as in an accumulating operation.

Higher speed cycles In predetermined operations, for example in therepeated adding or subtracting operations, some machine functions arenot effected. Particularly the engagement and disengagement of thesectors 14 with the racks 83, the tabulation stroke of the set upcarriage 11, its transverse restoration, and the printing, are to beeffected during a single operation and are to be prevented during theother operations. Since the engagement and disengagement of the sector14, as well as the return stroke of the carriage 11 are eifected by theauxiliary shaft 53, whereas the tabulation stroke of the carriage iseffected by the shaft 129, the cycles of said two shafts may be excludedbetween the various cycles of the main shaft 121.

Furthermore, since the printing requires a predetermined time betweenthe end of the forward stroke of the racks 83 and their return stroke,when the printing is excluded the main shaft 121 may be operated at ahigher speed. Therefore, the cycles wherein the printing is effectedwillbe called lower speed cycles, because the shaft 121 is operated at apredetermined low speed; the cycles whereinthe printing is excluded willbe called higher speed cycles because the shaft 121 is operated at aspeed higher than said predetermined speed.

In this order fulcrumed on the shaft 239 (FIG. 5) is a function controlmember formed of a lever 250 adapted to cooperate with the universal bar234 in a similar manner as the lever 238 (FIG. 4). The lever 250 may berocked counterclockwise through a partial stroke by manually orautomatically operable means. The lever 250 is connected through a link251 to a lever 252 fulcrumed on the shaft 148. The link 251 is providedwith a pin 253 normally contacted by a latch 255 under the urge of aspring 254. The latch 255 is fulcrumed on a pivot 256 and is adapted tocooperate with the lug 249 of the lever 144.

The lever 252 is pin and slot connected with a shifting member formed ofa lever 257 provided with a pair of shoulders 158 and 259 adapted toalternately cooperate with a pair of elements or lugs 260 and 261 of alever 262. This lever is fulcrumed on the shaft 148 and cooperates witha pair of cams 263 and 264 secured to the sleeve 153. Normally theshoulder 258 of the lever 257 lies into the path of the lug 260, whilethe shoulder 259 is out of the path of the lug 261.

The lever 257 is linked with a lug 266 of a horizontal lever 267 (FIG.3) fulcrumed on a pivot 268 and engaged by two flanges 269 secured tothe main shaft 121. This shaft is so mount-ed on the machine frame as tobe shifta'ble rightwards together with its cams and the crank lever 137,whereas the pinions 119 and 126 cannot be axially displaced therewith. Asecond main clutch is provided for causing the higher speed pinion119'to operate the main shaft 121. Said clutch comprises a second clutchpawl 271 (FIG. formed on the bail 13-8 and a clutch wheel 272 secured tothe pinion 119 (FIG. 3) the pawl 271 being normally located at left ofthe wheel 272.

The shaft 121 is provided with a group of normally ineffective camsadapted to cooperatewith the various cam followers of the machine whenthe shaft 121 is shifted rightwards. This second set of cams comprise apair of cams 273 and 274 (FIG. 3) for the bail 88 to operate theuniversal bars 87 and 100 (FIG. 1) substantially at the maximumpermissible speed for causing the racks 83 to correctly accumulate theset up amount into the totalizer 86 when the shaft 121 is rotated atsaid higher speed. The second group of cams comprises also a circulardisk 276 (FIG. 3) for the lever 134 to prevent the universal bar 109(FIG. 1) from being moved during the cycle of the shaft 121.

Upon rocking manually or automatically the lever 250 (FIG. 5) partiallycounterclockwise, the universal bar 234 causes the shaft 129 to effectone cycle in a manner similar to the lever 238 (FIG. 4). Then the link251 (FIG. 5) is partially displaced rearwards, whereby its pin 253causes the latch 255 to contact the lug 249 of the lever 144. During thecycle of the shaft 129 the lever 250 is fully rocked counterclockwiseand through the link 251 and the lever 252 displaces the lever 257 in avertical direction. The shoulder 259 is thus located into the path ofthe lug 261 of the lever 262, while the shoulder 258 is located out ofthe path of the lug 260.

At the end of the cycle of the shaft 129, the clutch 56, 57 (FIG. 6) isengaged to cause an auxiliary cycle of the shaft 53 and the sleeve 153.During the first part of this auxiliary cycle, the cams 263 and 264(FIG. 5) rock the lever 262 clockwise. Now the lug 261 engages theshoulder 259 and shifts the lever 257 forwards in a horizontaldirection. The lever 267 (FIG. 3) is rocked counterclockwise and shiftsthe main shaft 121 rightwards. Now, when the cam 166 (FIG. 6) rocks thebail 168 clockwise together with the lever 144, on one hand the lug 152of the lever 144 is placed into the path of the clutch pawl 56, wherebythe auxiliary shaft 53 is arrested at its intermediate position, on theother hand the lug 143 of the lever 144 releases the bail 138, wherebythe clutch pawl 271 (FIG. 5) engages the wheel 272.

The main shaft 121 is now rotated at a speed twice than in the case ofthe lower speed cycle, thus effecting a higher speed cycle. The lever144 is latched in the rocked position by the latch 255, whereby at theend of the cycle of the shaft 121 the clutch 271, 272 is not disengagedand clutch 56, 57 (FIG. 6) is not reengaged as long as the latch 255(FIG. 5) engages the lug 249. The main shaft 121 effects thus a set ofrepeated cycles, whereas the shaft 53 and the sleeve 153, as well as theshaft 129, are prevented from being cycled sequentially with therepeated cycles of the shaft 121. The latch 255 is caused to release thelug 249 of the lever 144- by means operated manually or automatically.Then the lever 144 may 'be restored counterclockwise and on one hand itslug 143 10 (FIG. 6) arrests the main shaft 121, on the other hand itslug 152 causes the clutch 56, 57 to be reengaged, whereby the shaft 53and the sleeve 153 may finally effect the second part of the auxiliarycycle.

The main shaft 121 may be returned leftwards to the position of thelower speed cycles, during an auxiliary cycle of the shaft 53 and thesleeve 153, when the lever 250 has not been rocked counterclockwise.Then the lug 260 engages the shoulder 258 of the lever 257, which isreturned rearwards, and through the lever 267 (FIG. 3) returns the shaft121 leftwards to the position of the lower speed cycles.

It is thus evident that the first cyclically operating mechanism 121 isnormally adapted to be operated at a predetermined speed sequentiallywith the second power operating mechanism 53, 153, and that the means257 are operable by the second mechanism 53, 153 under the control of afunction control member 250 for causing the first mechanism 121 to beoperated at a higher speed than said predetermined speed.

It will be understood that many changes, improvements and additions ofparts may be made to the described storing device without departing fromthe scope of the invention as defined in the appended claims thereof.

What I claim is:

1. In a printing calculating machine comprising a set of differentiallyreciprocable actuators, a power driving device having a main shaftcyclically power operable through a one-revolution main clutch foroperating said actuators, an auxiliary shaft cyclically power operablethrough a one-revolution auxiliary clutch for effecting predeterminedmachine functions, and a member operated by said auxiliary shaft forcausing said main shaft to be operated and for temporarily arrestingsaid auxiliary shaft in an intermediate position, the combinationcomprising:

(a) a normally effective first main clutch for driving said main shaftat a predetermined angular speed,

(b) a normally ineffective second main clutch for driving said mainshaft at an angular speed higher than said predetermined angular speed,

(c) a first group of cams on said main shaft,

(d) a group of cam followers normally cooperating with said first groupof cams for controlling said machine functions in a predeterminaterelationship with respect to the angular position of said main shaft,

(e) means operable for displacing said main shaft in an axial directionfor rendering said first main clutch and said first group of camsineffective and for rendering said second main clutch effective,

(f) a function control member,

(g) a shifting member controlled by said control member and operated bysaid auxiliary shaft for operating said displacing means,

(h) and a second group of cams on said main shaft adapted to cooperatewith said cam followers when said main shaft is so displaced forcontrolling said machine function in a different timing relationshipwith respect to said angular position.

2. In a printing calculating machine comprising a set of differentiallyreciprocable actuators, and a register adapted to cooperate with saidactuators for amount accumulating operations and total takingoperations, a power driving device having a cyclically power operablemain shaft, normally effective first cam means on said main shaft forcontrolling the reciprocation of said actuators, a cyclically poweroperable auxiliary shaft for effecting predetermined machine functions,means for causing said auxiliary shaft and said main shaft to besequentially cycled, and comprising in combination:

(a) a first clutch normally effective for operating said main shaft at apredetermined angular speed for enabling said normally effective cammeans to control the reciprocation of said actuators at the maximumpermissible speed for a correct cooperation with said register, 1

(b) a normally ineffective second clutch adapted to operate said mainshaft at an angular speed higher than said predetermined angular speed,

(c) normally ineffective second cam means on said main shaft, saidsecond cam means being so shaped as to control the reciprocation of saidactuators substantially at said maximum permissible speed upon operatingsaid main shaft at said higher angular speed,

'(d) a function control member,

(e) and means controlled by said member and operated by said auxiliaryshaft for rendering ineffective said first clutch and said first cammeans and for rendering effective said second clutch and said second cammeans.

3. A power driving device according to claim 2, comprising incombination:

(f) a cyclically power operating mechanism adapted to be operated upon apartial operation of said memher for causing the operation of saidauxiliary shaft,

(g) and means controlled by said mechanism for terminating the operationof said member.

4. A power driving device according to claim 2, comprising incombination:

(f) a starting member adapted to be moved by said function controlmember a predetermined extent,

(g) a cyclically power operating mechanism adapted to be operated bysaid starting member upon being so partially operated, said mechanismbeing adapted to cause said auxiliary shaft to be operated,

(h) means controlled by said mechanism for additionally moving saidstarting member and said control member,

(i) and means controlled by said control member when additionally movedand operated by said auxiliary shaft for rendering ineffective saidfirst clutch and said first cam means and for rendering effective saidsecond clutch and said second cam means.

5. In a printing calculating machine comprising a set of differentiallyreciprocable actuators, a register adapted to cooperate with saidactuators for amount accumulating operations and total takingoperations, and a printing device conditionable for printing amountsaccording to the differential reciprocation of said actuators, a powerdriving device having a cyclically power operable main shaft, a firstgroup of cams secured to said main shaft, cam following means normallyeffective for cooperation with said first group of cams to control thereciprocation of said actuators and to so condition said printingdevice, an auxiliary shaft cyclically power operable through aone-revolution auxiliary clutch for effecting predetermined machinefunctions, a member operated by said auxiliary shaft for causing saidmain shaft to be operated and for temporarily disengaging said auxiliaryclutch to arrest said auxiliary shaft in an intermediate position, andcomprising in combination:

(a) a first one-revolution main clutch'normally effective for operatingsaid main shaft at a predetermined angular speed for enabling said firstgroup of cams to control the reciprocation of said actuators at themaximum permissible speed for a correct cooperation with said register,

(b) a normally ineffective second clutch adapted to operate said mainshaft at an angular speed higher than said predetermined angular speed,

(c) a second group of cams normally axially distanced from said camfollowing means, said second group of cams when engaging said camfollowing means being adapted to prevent the operation of said printingdevice and to control the reciprocation of said actuators substantiallyat said maximum permissible speed upon operating said main shaft at saidhigher angular speed,

(d) a function control member for causing a machine operation wherein noprint is to be effected,

(e) means shiftably mounting said main shaft in axial direction,

(f) and a shifting'member controlled by said function control member andoperated by said auxiliary shaft for axially shifting said main shaft todisable said first main clutch and to engage said second main clutch,said first group of cams being then removed from said cam followingmeans, said second group of cams being caused to engage said camfollowing means.

6. In a ten key calculating machine comprising a set up mechanism, a setof actuators differentially reciprocable under the control of saidmechanism, a register adapted to cooperate with said actuators foramount accumulating operations and total taking operations, and aprinting device conditionable for printing amounts according to thedifferential reciprocation of said actuators, a power driving devicehaving a cyclically power operable main shaft, a first group of camssecured to said main shaft, cam following means normally effective forcooperation with said first group of cams to control the reciprocationof said actuators and to so condition said printing device, an auxiliaryshaft cyclically power operable through a one-revolution auxiliaryclutch, a set up control member operable by said keys for engaging saidauxiliary clutch to set up a figure on said mechanism, and comprising incombination:

(a) starting means for causing said auxiliary shaft to be oeprated foreffecting predetermined machine functions irrespective of said set upcontrol member,

(b) a member controlled by said starting means and operated by saidauxiliary shaft for causing said main shaft to be operated and fortemporarily disengaging said auxiliary clutch to arrest said auxiliaryshaft in an intermediate position,

(c) a first one-revolution main clutch normally effective for operatingsaid main shaft at a predetermined angular speed for enabling said firstgroup of cams to control the reciprocation of said actuators at themaximum permissible speed for a correct cooperation with said register,

(d) a normally ineffective second clutch adapted to operate said mainshaft at an angular speed higher than said predetermined angular speed,

(e) a second group of cams normally axially distanced from said camfollowing means, said second group of cams when engaging said camfollowing means being adapted to prevent the operation of said printingdevice and to control the reciprocation of said actuators substantiallyat said maximum permissible speed upon operating said main shaft at saidhigher angular speed,

(f) a function control member for causing a machine operation wherein noprint is to be effected,

(g) means shiftably mounting said main shaft in axial direction,

(h) and a shifting member controlled by said function control member andoperated by said auxiliary shaft for axially shifting said main shaft todisable said first main clutch and to engage said second main clutch,said first group of cams being then removed from said cam followingmeans, said second group of cams being caused to engage said camfollowing means.

7. In a printing calculating machine comprising a set of differentiallyreciprocable actuators, a register adapted to cooperate with saidactuators for amount accumulating operations and total takingoperations, and a printing device conditionable for printing amountsaccording to the differential reciprocation of said actuators, a powerdriving device having a cyclically power operable main shaft, a firstgroup of cams secured to said main shaft,

cam following means normally effective for cooperation with said firstgroup of cams to control the reciprocation of said actuators and to socondition said printing device, an auxiliary shaft cyclically poweroperable through a one-revolution auxiliary clutch for effectingpredetermined machine functions, an arresting member operated by saidauxiliary shaft for causing said main shaft to be operated and fortemporarily disengaging said auxiliary clutch to arrest said auxiliaryshaft in an intermediate position, and comprising in combination:

(a) a first one-revolution main clutch normally effective for operatingsaid main shaft at a predetermined angular speed for enabling said firstgroup of cams to control the reciprocation of said actuators at themaximum permissible speed for a correct cooperation with said register,

(b) a normally ineffective second clutch adapted to operate said mainshaft at an angular speed higher than said predetermined angular speed,

(c) a second group of cams normally axially distanced from said camfollowing means, said second group of cams when engaging said camfollowing means being adapted to prevent the operation of said printingdevice and to control the reciprocation of said actuators substantiallyat said maximum permissible speed upon operating said main shaft at saidhigher angular speed,

(d) means shiftably mounting said main shaft in axial direction,

(e) a normally ineffective latch for causing said arresting member tocondition said main shaft to effect repeated cycles,

(f) a displaceable control member,

(g) a shifting member controlled by said control member when sodisplaced for shifting said main shaft to disable said first main clutchand to engage said second main clutch, said first group of cams beingthen removed from said cam following means, said second group of camsbeing caused to engage said cam following means,

(h) and an element on said control member for rendering said latcheffective when said control member is so displaced, said elementdisabling said latch upon restoration of said control member, wherebysaid arresting member causes said auxiliary clutch to terminate thecycle of said auxiliary shaft.

8. In a ten key calculating machine comprising a set up mechanism, a setof actuators differentially reciprocable under the control of saidmechanism, a register adapted to cooperate with said actuators foramount accumulating operations and total taking operations, and aprinting device conditionable for printing amounts according to thedifferential reciprocation of said actuators, a power driving devicehaving a cyclically power operable main shaft, a first group of camssecured to said main shaft, cam following means normally effective forcooperating with said first group of cams to control the reciprocationof said actuators and to so condition said printing device, an auxiliaryshaft cyclically power operable through a one-revolution auxiliaryclutch, a set up control member operable by said keys for engaging saidauxiliary clutch to set up a figure on said mechanism, and comprising incombination:

(a) starting means for causing said auxiliary shaft to be operated foreffecting predetermined machine functions irrespective of said set upcontrol member,

(b) a member controlled by said starting means and operated by saidauxiliary shaft for .causing said main shaft to be operated and fortemporarily disengaging said auxiliary clutch to arrest said auxiliaryshaft in an intermediate position,

(c) a first one-revolution main clutch normally effective for operatingsaid main shaft at a predetermined angular speed for enabling said firstgroup of cams to control the reciprocation of said actuators at themaximum permissible speed for a correct cooperation with said register,

((1) a normally ineffective second clutch adapted to operate said mainshaft at an angular speed higher than said predetermined angular speed,

(c) a second group of cams normally axially distanced from said camfollowing means, said second group of cams when engaging said camfollowing means being adapted to prevent the operation of said printingdevice and to control the reciprocation of said actuators substantiallyat said maximum permissible speed upon operating said main shaft at saidhigher angular speed,

(f) a fun-ction control member for causing a machine operation whereinno print is to be effected,

(g) means shiftably mounting said main shaft in axial direction,

(h) a pair of elements cyclically operable by said aux iliary shaft,

(i) and a shifting member adapted to be moved by said control member ina first direction for being selectively engaged by one of said pair ofelements, said shifting member being shifted by said elements in asecond direction substantially perpendicular to said first direction forshifting said shaft to disable said first main clutch and to rendereffective said second main clutch, said first group of cams being thenremoved from said cam following means, said second group of cams beingcaused to engage said cam following means.

References Cited UNITED STATES PATENTS 2,340,261 1/ 1944 Eichler 235-622,399,890 5/1946 Pott 235-62 X 2,609,145 9/1952 Boyden et al 235-622,636,677 4/1953 Gang 235-62 3,072,329 1/ 1963 Dodsworth 235-623,116,873 1/1964 Trumpelmann et al. 235-63 STEPHEN I. TOMSKY, PrimaryExaminer.

1. IN A PRINTING CALCULATING MACHINE COMPRISING A SET OF DIFFERENTIALLYRECIPROCABLE ACTUATORS, A POWER DRIVING DEVICE HAVING A MAIN SHAFTCYCLICALLY POWER OPERABLE THROUGH A ONE-REVOLUTION MAIN CLUTCH FOROPERATING SAID ACTUATORS, AN AUXILIARY SHAFT CYCLICALLY POWER OPERABLETHROUGH A ONE-REVOLUTION AUXILIARY CLUTCH FOR EFFECTING PREDETERMINEDMACHINE FUNCTIONS, AND A MEMBER OPERATED BY SAID AUXILIARY SHAFT FORCAUSING SAID MAIN SHAFT TO BE OPERATED AND FOR TEMPORARILY ARRESTINGSAID AUXILIARY SHAFT IN AN INTERMEDIATE POSITION, THE COMBINATIONCOMPRISING: (A) A NORMALLY EFFECTIVE FIRST MAIN CLUTCH FOR DRIVING SAIDMAIN SHAFT AT A PREDETERMINED ANGULAR SPEED, (B) A NORMALLY INEFFECTIVESECOND MAIN CLUTCH FOR DRIVING SAID MAIN SHAFT AT AN ANGULAR SPEEDHIGHER THAN SAID PREDETERMINED ANGULAR SPEED, (C) A FIRST GROUP OF CAMSON SAID MAIN SHAFT, (D) A GROUP OF CAM FOLLOWERS NORMALLY COOPERATINGWITH SAID FIRST GROUP OF CAMS FOR CONTROLLING SAID MACHINE FUNCTIONS INA PREDETERMINATE RELATIONSHIP WITH RESPECT TO THE ANGULAR POSITIONS OFSAID MAIN SHAFT, (E) MEANS OPERABLE FOR DISPLACING SAID MAIN SHAFT IN ANAXIAL DIRECTION FOR RENDERING SAID FIRST MAIN CLUTCH AND SAID FIRSTGROUP OF CAMS INEFFECTIVE AND FOR RENDERING SAID SECOND MAIN CLUTCHEFFECTIVE, (F) A FUNCTION CONTROL MEMBER, (G) A SHIFTING MEMBERCONTROLLED BY SAID CONTROL MEMBER AND OPERATED BY SAID AUXILIARY SHAFTFOR OPERATING SAID DISPLACING MEANS, (H) AND A SECOND GROUP OF CAMS ONSAID MAIN SHAFT ADAPTED TO COOPERATE WITH SAID CAM FOLLOWERS WHEN SAIDMAIN SHAFT IS SO DISPLACED FOR CONTROLLING SAID MACHINE FUNCTION IN ADIFFERENT TIMING RELATIONSHIP WITH RESPECT TO SAID ANGULAR POSITION.